JP2001018861A - Crawler vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To simplify a work removing mud during maintenance by preventing mud from accumulating between a track frame and a crawler. SOLUTION: Mud covers 21 are placed tilted in a crosswise direction between a track frame 7 and a crawler of a lower traveling body. The mud covers 21 are mounted on a center frame 8 through plate springs 23. A hydraulic cylinder 24 is provided on the center frame 8. The mud covers 21 are attached to both ends of a rod 24C of the hydraulic cylinder 24. By extending/retracting the rod 24C of the hydraulic cylinder 24 for vibration, the mud covers 21 is oscillated in a crosswise horizontal direction. This motion will apply an inertial force in two directions, the slant direction and the thickness direction orthogonal to the slant direction, on mud dropped on the mud covers 21, thereby smoothly exhausting the mud along the slant direction of the mud covers 21.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a tracked vehicle suitably used for a construction machine having a crawler, such as a hydraulic shovel or a hydraulic crane.

[0002]

2. Description of the Related Art In general, a tracked vehicle used for construction equipment such as a hydraulic excavator includes a track frame provided with a pair of side frames on both left and right sides of a center frame, and a front and rear direction of the side frames. An idler wheel provided on one side, a drive wheel provided on the other side in front of and behind the side frame, a crawler belt provided between the idler wheel and the drive wheel, An upper roller and the like are provided on the upper surface side of the side frame and guide the crawler belt.

[0003] In this kind of tracked vehicle according to the prior art, a driving wheel provided on a side frame of a truck frame is driven to rotate by a hydraulic motor for traveling or the like, and a crawler belt circulates between an idler wheel and a driving wheel. This causes the vehicle to move forward or backward.

By the way, in a tracked vehicle according to the prior art, when traveling on muddy ground, for example, mud and the like scraped up by the crawler belt often accumulate between the side frame and the crawler belt. The smooth rotation of the upper roller is hindered by the mud, so that the movement of the crawler belt is deteriorated, and the running property is easily reduced.

On the other hand, as another prior art, a soil discharging member is provided on each of the idler wheel side and the driving wheel side of the side frame, and the mud adhering to the inside of the crawler belt is scraped by the discharging member when the crawler belt is driven. It is known that the liquid is discharged so as to be dropped (for example, Japanese Patent Application Laid-Open No. 8-31045).
No. 7).

In this prior art, earth discharging members provided on the idle wheel side and the drive wheel side of the side frame, respectively,
It operates so as to scrape off the mud in contact with the mud attached to the inside of the crawler belt, thereby preventing the mud from accumulating between the side frame and the crawler belt.

[0007]

By the way, in the other prior arts described above, since the side frame is merely provided with a soil discharging member, the mud adhering to the crawler belt when traveling on, for example, a muddy ground is sufficiently removed. It is difficult to remove the soil, and mud often accumulates between the crawler belt and the upper surface of the side frame.

In particular, when the vehicle travels on a soft ground made of mud having a high viscosity such as the Kanto loam layer, the mud may be tightly packed in the gap between the track frame and the crawler belt. In this case, there is a problem that the appearance quality of a tracked vehicle such as a hydraulic shovel or the like is remarkably deteriorated by the mud and the commercial value is reduced for a leasing company or a rental company.

Further, since mud accumulated between the side frame and the crawler belt hinders smooth rotation of the upper roller, it is necessary to remove the mud using, for example, washing water or a scoop. Has the problem of spending a lot of time and effort.

Further, in a cold region or the like, if the mud accumulated between the side frame and the crawler belt becomes frozen soil, it is extremely difficult to remove the mud. In particular,
The muddy water and the like jumped up by the crawler belt adhere to the space between the crawler belt and the upper roller and freeze, thereby hindering the smooth operation of the crawler belt and the upper roller and performing a stable traveling operation. There is a problem that it becomes difficult.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems of the prior art, and an object of the present invention is to suppress the accumulation of mud and the like between the track frame and the crawler belt and prevent the appearance quality from deteriorating. It is another object of the present invention to provide a tracked vehicle capable of simplifying the work of removing mud and ensuring stable running performance for a long period of time.

[0012]

In order to solve the above-mentioned problems, a tracked vehicle according to the present invention comprises: a track frame provided with side frames on both left and right sides of a center frame; An idler wheel provided on one side in the rear direction, a drive wheel provided on the other side in front of and behind the side frames, and a crawler belt wound between the idler wheel and the drive wheel. A mudguard cover provided on the track frame and positioned between the upper surface of the side frame and the crawler belt to cover the track frame from above.

A feature of the structure adopted by the first aspect of the invention is that the mudguard cover is disposed obliquely downward and leftward and rightward from the center frame to the side frame,
Between the track frame and the mudguard cover, a vibration actuator for vibrating the mudguard cover in the left and right horizontal directions is provided.

With this configuration, when the mud falls and adheres to the mudguard cover, the mudguard cover obliquely arranged in the left and right directions is vibrated in the left and right horizontal directions by the vibration actuator. The inertia force can be applied to the mud in the plate thickness direction (the direction perpendicular to the inclination direction) in addition to the inclination direction of the mudguard cover, and the inertial force in the thickness direction allows the mudguard cover to act on the mud. The frictional force (perpendicular force) can be reduced, and mud can be discharged smoothly along the mudguard cover.

According to the second aspect of the present invention, the vibrating actuator comprises a hydraulic cylinder which repeatedly expands and contracts the rod in the left and right horizontal directions from the tube by repeatedly supplying and discharging pressure oil from the outside, The hydraulic cylinder attaches the tube to the center frame side, and the rod attaches to the mudguard cover so that the mudguard cover vibrates in the horizontal direction.

Thus, when pressure oil is repeatedly supplied and discharged from the outside to the hydraulic cylinder, the mudguard cover can be vibrated in the left and right horizontal directions at high speed in accordance with the expansion and contraction operation of the hydraulic cylinder.

A feature of the construction adopted by the invention of claim 3 is that the mudguard cover is disposed obliquely downward and leftward and rightward from the center frame to the side frame side, so that the track frame and the mudguard cover are separated from each other. In between, a first vibration actuator that vibrates the mudguard cover in an inclined direction and a second vibration actuator that vibrates the mudguard cover in a direction different from the first vibration actuator. The configuration is provided.

According to this structure, when the mud falls onto the mudguard cover, the first and second vibrating actuators are actuated so that the mudguard cover is tilted in the same direction as in the first aspect of the present invention. It can vibrate in the thickness direction, and can discharge the mud smoothly along the inclination direction of the mudguard cover.

According to the fourth aspect of the present invention, the first and second vibrating actuators vibrate the mudguard cover with a phase difference from each other, thereby applying vibration for giving an elliptical motion to the mudguard cover. ing.

In this case, by driving the first and second vibrating actuators with a phase difference from each other, the mudguard cover repeatedly vibrates in a circular or elliptical locus on the track frame. become,
Mud can be efficiently discharged from the mudguard cover.

Further, according to a fifth aspect of the present invention, the first vibration actuator vibrates the mudguard cover in an inclined direction,
The second vibrating actuator vibrates the mudguard cover in the tilt direction and the plate thickness direction, and the first and second vibrating actuators vibrate with a phase difference of 90 degrees from each other. , A vibration that gives a circular motion or an elliptical motion is added.

In this case, the first and second vibrating actuators can be driven with a phase difference of 90 degrees from each other, so that a circular or elliptical vibration can be stably applied to the mudguard cover. can do.

On the other hand, a feature of the structure adopted by the invention of claim 6 is that the mudguard cover is provided between the track frame and the mudguard cover and is repeatedly oscillated by supplying and discharging pressure oil from a hydraulic source. A vibration actuator, and a pressure oil provided between the vibration actuator and a hydraulic pressure source, which is supplied to and discharged from the vibration actuator, allows the vibration actuator to move quickly on one side in the vibration direction to the other side. And an actuator control means for driving the actuator slowly.

With this configuration, when the mud falls onto the mudguard cover, the actuator control means controls the pressure oil supplied / discharged from the hydraulic source to the vibrating actuator, and moves the vibrating actuator in the vibration direction. By driving at different speeds on one side and the other side, the inertial force applied to the mud can be changed between one side and the other side in the vibration direction. Then, a slip can be generated between the mud and the mudguard cover due to the change in the inertial force, and the mudguard cover can be smoothly discharged along the inclination direction of the mudguard cover.

According to a seventh aspect of the present invention, the actuator control means is configured to change the movement when the mudguard cover is displaced from the side frame to the side of the center frame by the vibrating actuator when the cover is displaced from the center frame to the side frame. The supply / discharge of the pressure oil to / from the vibrating actuator is controlled so as to be faster than the movement.

Accordingly, when the mudguard cover is displaced from the side frame to the center frame side (inward in the left and right directions), the mudguard cover can be driven at a high speed, and an inertial force is applied in a direction in which the mud is separated from the mudguard cover. be able to. Then, the mud is separated from the mudguard cover by the inertial force at this time, the adhesive force of the mud is reduced, and the mud can be discharged to the side frame side (outside in the left and right directions) along the mudguard cover.

The mudguard cover is moved from the center frame to the side frame side (left,
When displacing to the right (outward in the right direction), by slowly driving the mudguard cover, the inertial force toward the center frame (left and right inward) added to the mud at this time can be reduced. The mud can be maintained in a state of being stopped on the mudguard cover without sliding the mud toward the center frame.

According to the invention of claim 8, the mudguard cover is disposed to be inclined obliquely downward left and right from the center frame to the side frame side, and the vibrating actuator moves the mudguard cover in the inclined direction. The actuator control means is configured by a vibrating actuator, and the movement when the mudguard cover is displaced from the side frame to the side of the center frame by the vibrating actuator is different from the movement when the cover is displaced from the center frame to the side frame. Also, the supply and discharge of the pressure oil to and from the vibrating actuator are controlled so as to increase the speed.

In this case, since the mudguard cover is arranged obliquely downward and leftward and rightward from the center frame to the side frame, the mudguard cover is vibrated in the inclined direction by the vibration actuator. Thereby, the mud can be discharged more smoothly along the mudguard cover.

On the other hand, according to a ninth aspect of the present invention, the actuator control means is provided in the middle of a pair of pipelines connecting the vibration actuator to a hydraulic source, and the vibration actuator is controlled in response to an external control signal. And a signal output means for outputting the control signal to the vibration control valve as a signal having a sawtooth waveform.

As a result, a control signal having a sawtooth waveform is output from the signal output means to the vibration control valve, so that the vibration control valve is switched substantially in accordance with the control signal waveform. The vibration actuator can be moved quickly on one side of the left and right sides and slowly moved on the other side by the switching operation of the solenoid valve.

According to a tenth aspect of the present invention, the actuator control means is provided in the middle of a pair of pipes connecting the vibration actuator to a hydraulic pressure source, and switches the supply / discharge direction of the pressure oil to and from the vibration actuator. A control valve for excitation,
A slow return valve provided in the middle of the conduit to provide a throttle effect on pressure oil discharged from the vibration actuator when the vibration actuator is displaced to the other side in the vibration direction. I have.

Accordingly, when the vibration actuator is displaced to one side in the vibration direction, the vibration actuator can be driven faster by the check valve of the slow return valve. On the other hand, when the vibration actuator is displaced to the other side in the vibration direction, a slow return valve gives a throttling effect to the pressure oil discharged from the vibration actuator, and the vibration actuator is driven slowly. Can be.

According to the eleventh aspect of the present invention, in the vibration actuator, the tube attached to the center frame side, the base end side is inserted into the tube, and the distal end side protrudes out of the tube, and is attached to the mudguard cover. Rod, a piston provided on the base end side of the rod and slidably inserted into the tube, and provided in the tube by the piston to give different pressure receiving areas to the piston. Composed of two oil chambers,
The actuator control means is provided halfway between a pair of pipelines connecting the hydraulic cylinder to a hydraulic pressure source, and supplies pressurized oil to the larger one of the two oil chambers having a smaller pressure receiving area. A vibration control valve selectively switched between a first switching position for discharging the pressure oil from the oil chamber side and a second switching position for supplying the pressure oil to both of the oil chambers. I have.

Thus, when the vibration control valve is switched to the first switching position, the pressure oil is supplied to the oil chamber having the smaller pressure receiving area, and the pressure oil is discharged from the oil chamber having the larger pressure receiving area. Therefore, for example, the rod can be displaced more slowly due to the relationship of the pressure receiving area, and the inertial force applied to the mud can be reduced to a small extent. Further, when the vibration control valve is switched to the second switching position, the pressure oil is supplied to both oil chambers, and for example, the rod can be rapidly displaced by a difference in pressure receiving area between the two oil chambers. The inertial force can be increased.

Further, in the twelfth aspect of the present invention, a water-repellent film is formed on the surface side of the mudguard cover. Thereby, the mud and the like can be prevented from adhering to the surface side of the mudguard cover by the water-repellent film, and the mud and the like can be quickly discharged to the outside by applying vibration to the mudguard cover.

Further, according to a thirteenth aspect of the present invention, the mudguard cover is divided into a plurality of sheets in the front and rear directions or in the left and right directions.
Each of these covers is integrally connected to each other using a connecting tool. By this, when attaching the mudguard cover, each cover is separately attached to the track frame in advance, and in this state, the covers can be integrally connected to each other using the connecting tool, so that the work of attaching the mudguard cover can be easily performed. it can.

[0038]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an example in which a tracked vehicle according to an embodiment of the present invention is applied to a hydraulic shovel will be described.
This will be described in detail with reference to the accompanying drawings.

Here, FIGS. 1 to 10 show the first embodiment of the present invention.
In the drawings, reference numeral 1 denotes a lower traveling body, 2 denotes an upper revolving body that is rotatably mounted on the lower traveling body 1, and the upper revolving body 2 is, for example, a building cover containing a motor and the like. 3. Cab 4 and counterweight 5 as cab
And the like. A working device 6 for excavating soil and the like is provided at the front of the upper swing body 2 so as to be able to move up and down.

Reference numeral 7 denotes a track frame constituting the main body of the lower traveling body 1. The track frame 7 is formed by welding a steel plate or the like as shown in FIGS. And side frames 11, 11 provided on both the left and right sides of the center frame 8 and extending in the front and rear directions, which will be described later.

Here, the center frame 8 corresponds to FIGS.
As shown in the figure, a circular cylinder 9 is formed at the center, and legs 10 extending in the front, rear, left, and right directions from the outer peripheral side of the circular cylinder 9 and forming an H shape as a whole. And the leg 10 is
Upper plate portion 10A, lower plate portion 10B and these plate portions 10
A and 10B are formed as a can-made structure by a side plate portion 10C which is connected in the upper and lower directions.

Reference numerals 11 and 11 denote legs 10 of the center frame 8.
Left and right side frames provided by welding on the left and right sides of the left and right sides of FIG.
As shown in the figure, the frame is formed as a substantially U-shaped frame extending in the front and rear directions. The side plate 11 has an upper plate portion 11A in which the left and right widthwise middle portions are bent in a V shape.
And an inner side plate 11B extending downward from the widthwise inner end (left end in FIG. 5) of the upper plate 11A, and extending downward from the widthwise outer end of the upper plate 11A. The outer side plate portion 11C is generally configured.

An end plate 12 is provided at one end in the front and rear directions of the side frame 11, and an idler wheel bracket 13 is integrally provided on the end plate 12. An end plate 14 is provided at the other end of the side frame 11 in the front and rear directions.
The end plate 14 is integrally provided with a drive wheel bracket 15.

Reference numeral 16 denotes an idler wheel which is located on one side in the front and rear directions of the side frame 11 and is rotatably provided on the idler wheel bracket 13, and 17 is located on the other side of the front and rear sides of the side frame 11. The driving wheels provided on the driving wheel bracket 15 are driven to rotate by a traveling hydraulic motor (not shown) or the like.

Reference numeral 18 denotes left and right crawler belts (only one of which is shown) wound between the idler wheel 16 and the drive wheel 17. The crawler belt 18 is provided between the idler wheel 16 and the drive wheel 17. The upper and lower sides of the side frame 11 extend forward and rearward. The crawler belt 18 travels and drives the lower traveling body 1 by rotationally driving the drive wheels 17 with a traveling hydraulic motor.

Reference numerals 19, 19 denote upper rollers provided on the upper plate portion 11A of the side frame 11 so as to be separated from each other in front and behind. Each upper roller 19 guides the crawler belt 18 above the side frame 11, and smoothly moves the crawler belt 18. It compensates for the unnatural movement.
Reference numerals 20, 20,... Denote lower rollers provided on the lower side of the side frame 11. Each lower roller 20 guides the crawler belt 18 below the side frame 11, thereby increasing the contact area of the crawler belt 18 with the ground. Track 18 along the ground
Is operated smoothly.

Reference numerals 21 and 21 denote side frames 11 and crawler tracks 1.
8 and a mudguard cover 21 provided on the upper plate portion 11A. These mudguard covers 21 are made of a plate body such as a steel plate as shown in FIGS. From the 8 side to each side frame 11 side, it extends obliquely downward to the left and right at an angle θ shown in FIG.

These mudguard covers 21 partially cover the legs 10 (upper plate 10A) of the center frame 8 on the left and right sides of the round body 9 from above, and also cover the upper surface of each side frame 11. Over almost the entire length.

Here, the mudguard cover 21 is shown in FIGS.
As shown in the figure, the side frame 11 is displaceably mounted on an upper plate portion 11A of the side frame 11 by using a leaf spring 23 described later, and is repeatedly vibrated by a hydraulic cylinder 24. Further, the mudguard cover 21 is an inner end 21A in the left and right directions.
Extends along the leg 10 (upper plate 10A) of the center frame 8 to a position close to the round body 9, and has an outer end 21B
Are the upper plate 11A and the side plate 11C of the side frame 11.
And extends to a position on the corner of the corner.

Further, in the middle part in the width direction of the mudguard cover 21, substantially rectangular notches 21C, 21C are formed at positions corresponding to the respective upper rollers 19 as shown in FIGS. The portion 21C also allows the mudguard cover 21 to move the upper roller 1 when the vibrating operation of the mudguard cover 21 is performed.
9 to avoid interference.

Thus, the left and right mudguard covers 21 and 2
1 is disposed obliquely downward from the center frame 8 side toward the outside in the width direction of the side frame 11, and covers the upper plate portion 10 </ b> A of the leg 10 and the side frame 11 from above, so that the crawler belt 18 will be described later. To prevent the mud 30 scooped up from falling on the upper plate portion 10A and the side frame 11 of the leg 10 and to move the mud 30 to the outside along the inclination direction of the mudguard cover 21 with a vibration operation described later. Is to be discharged.

As shown in FIG. 5, a coating layer 22 is formed on the surface of the mudguard cover 21 as shown in FIG. When the mud 30 adhered to the crawler belt 18 falls on the mudguard cover 21, the mud 30
Has a function of smoothly discharging to the outside along the inclination direction of the mudguard cover 21.

Are plate springs provided between the upper plate portion 11A of the side frame 11 and the mudguard cover 21. The plate springs 23 are made of, for example, spring steel or the like as shown in FIGS. , And are arranged at intervals in the length direction of the side frame 11.
The upper and lower ends of the leaf spring 23 are fixed to the upper plate portion 11A and the mudguard cover 21 of the side frame 11, respectively, and the mudguard cover 21 can be displaced on the side frame 11 as shown in FIGS. It is configured to support.

Numerals 24, 24 denote hydraulic cylinders provided as a vibration actuator provided between the center frame 8 and the mudguard cover 21. These hydraulic cylinders 24 are located in front of the round cylinder 9 as shown in FIG. A total of two pieces are arranged on the legs 10 of the center frame 8 at a later distance.

Here, the hydraulic cylinder 24 is composed of a tube 24A attached to the legs 10 of the center frame 8 in the left and right directions, and an annular piston 24B slidably inserted in the tube 24A (see FIG. 6) and rods 24C which are fixed to the inner peripheral side of the piston 24B in an inserted state and whose left and right ends project outside the tube 24A to the left and right, respectively. The piston 24B is formed of a tube 24A. Is defined by two oil chambers 24D and 24E.

The hydraulic cylinder 24 has a rod 24C.
The protruding end side is, for example, a bifurcated mounting bracket 24F. The mudguard cover 21 is fastened to the mounting bracket 24F by sandwiching the inner end 21A of the mudguard cover 21 between the mounting bracket 24F.

The hydraulic cylinder 24 is supplied with pressure oil to and from the oil chambers 24D and 24E via a vibration control valve 28, which will be described later. The entire 21 is vibrated horizontally in the left and right directions in the directions indicated by arrows a and a 'shown in FIG. In this case, the vibration frequency applied to the mudguard cover 21 is desirably set to, for example, about 20 to 100 Hz.

As described later, the hydraulic cylinder 24 moves the mudguard cover 21 in an inclined direction (X-axis direction in FIG. 5) and a plate thickness direction orthogonal to the inclined direction of the mud cover 21 (Y-axis in FIG. 5). Direction).

Here, in the hydraulic cylinder 24, when the stroke amount of the rod 24C in the left and right horizontal directions is S, the relationship between the time t and the stroke amount S is set as in the following equation (1). (See FIG. 9).

[0060]

S = A × sin (ω × t−π / 2) Amplitude: A Angular velocity: ω

In equation (1), the stroke amount S when the rod 24C is located at an intermediate position between the most extended position and the most reduced position is set to zero. FIG. 9 shows the rod 2
When 4C is displaced from the intermediate position in the extension direction, it is defined as positive,
It is defined as negative when displaced in the reduction direction.

Next, a control circuit for controlling the operation of the hydraulic cylinder 24 will be described with reference to FIG.

A hydraulic pump 25 constitutes a hydraulic source together with a tank 26. The hydraulic pump 25 is housed in the building cover 3 of the upper revolving unit 2, and is rotated by a motor to operate the tank 26. The oil is supplied to and discharged from the hydraulic cylinder 24, a traveling hydraulic motor, and the like as high-pressure oil.

Reference numerals 27A and 27B denote oil chambers 24D and 24E of the hydraulic cylinder 24, respectively.
, A pair of conduits 28 connected to these conduits 27A, 2
This is a vibration control valve provided in the middle of 7B, and the vibration control valve 28 is constituted by, for example, an electromagnetic directional control valve having a 4-port 3-position or 4-port 2-position.

The vibration control valve 28 is controlled, for example, by a control signal from a controller (not shown) or the like.
The switching control is continuously performed with a cycle of about 100 Hz.
4C is subjected to repeated stretching vibration.

Reference numeral 29 designates the hydraulic cylinder 24 as the hydraulic pump 25
The switching valve 29 is a switching valve provided in the middle of a pipe line 27B connected to the motor. The switching valve 29 is a two-port, two-position spring return type hydraulic pilot type switching valve. A part is supplied to the hydraulic pilot unit 29A as pilot pressure.

When the pilot pressure is supplied to the hydraulic pilot portion 29A, the switching valve 29 is normally set at the valve closing position (a) where the hydraulic cylinder 24 is shut off from the hydraulic pump 25. This is for switching the cylinder 24 to the valve opening position (b) for connecting to the hydraulic pump 25. Thus, the hydraulic cylinder 24 is operated to extend and contract by the switching valve 29 only during traveling.

The tracked vehicle according to the present embodiment has the above-described configuration. When the vehicle travels on the road, the drive wheels 17 are rotated by the traveling hydraulic motor, so that the crawler belt 18 and the idler wheels 16 and the drive wheels 17 are rotated. Circulating between and
This causes the vehicle to move forward or backward.

By the way, when the vehicle travels on soft ground such as muddy ground, which is made of high-viscosity mud, the mud tends to accumulate between the track frame 7 and the crawler belt 18, and the smooth orbiting operation of the crawler belt 18 is hindered. There is a fear. Further, even when traveling in a cold region or the like, muddy soil is deposited as frozen soil between the track frame 7 and the crawler belt 18 and the crawler 1
8 may hinder the smooth orbiting operation.

Therefore, in the present embodiment, the undercarriage 1
Between the track frame 7 and the crawler belt 18, the left and right mudguard covers 21, 21 are inclined obliquely downward toward the left and right outer sides, and these mudguard covers 21 are moved to the left and right by hydraulic cylinders 24. By vibrating at high speed in the right horizontal direction (arrows a and a 'directions), the mud 30 dropped on the mud cover 21 as shown in FIG.
1 is configured to be discharged in the inclination direction.

Here, the relationship between the forces acting on the mud 30 on the mudguard cover 21 when the mudguard cover 21 is stopped from oscillating will be described with reference to FIG.

First, assuming that the mass of the mud 30 is m and the gravitational acceleration is g, the gravity W (W = m ×
g) acts, and the X-axis direction component WX and the Y-axis direction component WY of the gravity W

[0073]

## EQU2 ## WX = W.times.sin .theta.

[0074]

## EQU3 ## WY = W.times.cos .theta.

The mud 30 is covered with a mudguard cover 2.
From 1, a reaction force N (N = WY) as a vertical reaction due to the Y-axis direction component WY of gravity W acts. Further, a frictional force P acts on the mud 30 with the mudguard cover 21 by the reaction force N, and the frictional force P is

[0076]

## EQU4 ## P = μ × WY = μ × W × cos θ μ: friction coefficient

Next, the relationship between the forces acting on the mud 30 when the mudguard cover 21 is vibrated by the hydraulic cylinder 24 will be described with reference to FIGS.

First, since the hydraulic cylinder 24 expands and contracts with the characteristics of the equation 1, the relationship between the vibration acceleration α of the mudguard cover 21 and the time t is set as shown in the following equation 5 (FIG. 1).
0).

[0079]

Α = −A × ω ² × sin (ω × t−π / 2)

Since the mudguard cover 21 is inclined at an angle θ, the vibration acceleration αX in the inclination direction (X-axis direction) and the vibration acceleration αY in the thickness direction (Y-axis direction) of the mudguard cover 21 are: ,Respectively

[0081]

ΑX = −A × ω ² × cos θ × sin (ω × t
-Π / 2)

[0082]

ΑY = −A × ω ² × sin θ × sin (ω × t
−π / 2).

For this reason, the mud 30 is covered with the mudguard cover 21.
, An inertial force f apparently opposite to the vibration acceleration α is added, and the magnitude of the inertial force f is

[0084]

[Mathematical formula-see original document] f = m * (-[alpha]), and the X-axis component fx and the Y-axis component f of the inertial force f
Y has each size,

[0085]

## EQU9 ## fx = mx.times. (-. Alpha.x)

[0086]

## EQU10 ## fY = m.times. (-. Alpha.Y).

Thus, in the present embodiment, as shown in FIG. 7, the rod 24C of the hydraulic cylinder 24 moves from the minimum contraction position to the intermediate position (corresponding to the section a1 in FIGS. 9 and 10) in the direction of arrow a '. ), The vibration acceleration α of the mudguard cover 21 (rod 24C) is positive (see FIG. 10), so that both the vibration acceleration αX in the X-axis direction and the vibration acceleration αY in the Y-axis direction are positive.

For this reason, the inertia force fx (see Equation 9) is applied to the mud 30 in the negative direction of the X axis, and the mud 30 tends to slide diagonally upward along the mudguard cover 21. However, the mud 30 has an inertia force fY in the negative direction of the Y axis.
(See Equation 10), the mud 30 can be strongly pressed against the surface of the mudguard cover 21 by this inertial force fY.
The movement of the mudguard cover 21 can be followed in a state where the mudguard cover 21 is stopped on the mudguard cover 21, and the mud 30 can be prevented from sliding diagonally upward along the mudguard cover 21 as described above.

On the other hand, while the rod 24C of the hydraulic cylinder 24 extends from the intermediate position to the maximum extension position (corresponding to the section a2 in FIG. 9) in the direction of arrow a as shown in FIG. Since the vibration acceleration α is negative (see FIG. 10), the vibration acceleration αX in the X-axis direction and the vibration acceleration αY in the Y-axis direction are both negative.

For this reason, as shown in FIG. 8, an inertial force fx is applied to the mud 30 in the positive direction of the X axis, and the mud 30 can be separated from the mudguard cover 21 and slid in the inclined direction. In addition, since the inertia force fY can be applied to the mud 30 in the positive direction of the Y axis, the pressing force of the mud 30 against the surface of the mud cover 21 is reduced, and the friction acting between the mud 30 and the mud cover 21 is reduced. The force can be reduced, so that the mud 30 can be slid smoothly in the inclined direction of the mud cover 21 and discharged to the outside, and the discharge efficiency of the mud 30 can be increased.

Further, as shown in FIG.
Is reduced from the maximum extension position to the intermediate position (corresponding to the section a3 in FIGS. 9 and 10) in the direction indicated by the arrow a ', as in the case of the section a2, the vibration acceleration .alpha. Since it becomes negative, the mud 30 is covered with the mud cover 21.
Can be discharged smoothly along the inclination direction of

Further, as shown in FIG. 7, the rod 24C is moved from the intermediate position to the minimum contraction position in the direction of arrow a (FIGS. 9 and 10).
(Corresponding to the middle section a4), the vibration acceleration α of the mudguard cover 21 becomes positive as in the case of the section a1 described above, so that the mud 30 remains stopped on the mudguard cover 21. Thus, the movement of the mudguard cover 21 can be followed.

Therefore, according to the present embodiment, the hydraulic cylinder 2 is applied to the mud 30 dropped on the mudguard cover 21.
4, the inertia force in the thickness direction (Y-axis direction) orthogonal to the inclination direction can be applied in addition to the inertia force in the inclination direction (X-axis direction) of the mudguard cover 21. Only in the X-axis direction)
The mud 30 can be more smoothly discharged as compared with a configuration in which only the inertia force in the inclined direction is applied to the mud 30 on the mud cover 21.

The vibration direction of the mudguard cover 21 is set to the left,
Since the rightward direction is set, the possibility that so-called vibration nodes are formed is reduced as compared with the case where the mudguard cover 21 is vibrated only in the thickness direction (Y-axis direction), for example. The whole can be evenly vibrated, and the mud 30 can be efficiently discharged from the surface side of the mudguard cover 21.

Thus, the truck frame 7 can be moved during traveling.
Can prevent the accumulation of mud 30, frozen soil, and the like between the crawler belt 18 and the crawler belt 18, greatly simplify the work of removing the mud 30 performed during maintenance work of the excavator, and provide a hydraulic excavator rental company. Thus, the burden on the leasing company and the like can be reduced, the car washing operation and the like can be performed efficiently, and the workability at the time of maintenance can be improved.

Since the hydraulic excavator can be kept in a clean state, its appearance quality can be improved and its commercial value can be increased. After maintenance, the crawler belt 18 is moved between the driving wheel 17 and the idler wheel 16 by the upper roller 1.
Since the drive can be performed smoothly through the driving mechanism 9 and the like, mechanical friction loss and the like during traveling can be reduced, traveling performance can be surely improved, and safety during traveling can be enhanced.

Further, since the coating layer 22 made of a water-repellent coating is formed on the surface side of the mudguard cover 21, even if the viscous mud 30 falls on the mudguard cover 21, the coating layer 22 is used. The mudguard cover 2 can be used without adhering the mud 30 to the mudguard cover 21.
1 can be slid along the inclined direction, and the mud 30 can be discharged better.

Further, in the present embodiment, a pipeline 27 connecting the hydraulic cylinder 24 to the hydraulic pump 25 and the tank 26
A switching valve 29 is provided in the middle of A and 27B, and the switching valve 29 is switched from the valve closing position (A) to the valve opening position (B) only during traveling, so that the hydraulic cylinder 24 is automatically operated only during traveling. When the vehicle is stopped, noise caused by the operation sound of the hydraulic cylinder 24 is eliminated, so that noise can be reduced and energy can be saved.

Further, when the vehicle is traveling or when traveling is stopped, it is possible to eliminate the trouble that the operator has to manually operate the hydraulic cylinder 24, for example, to manually switch the hydraulic cylinder 24. And the like.

The mudguard cover 21 has an upper roller 19
The notch 21C is provided at a position corresponding to. For this reason, when attaching the mudguard cover 21 to the side frame 11 and further when performing the vibration operation, the notch 21
C can prevent the mudguard cover 21 from interfering with the upper roller 19, and
Maintenance work can be easily performed.

The hydraulic cylinder 24 is connected to the tube 24
A, the mudguard cover 21 can be made to vibrate at high speed by utilizing the expansion and contraction operation of the rod 24C because the actuator is configured by using the vibration actuator composed of the piston A, the piston 24B, and the rod 24C. Can be executed efficiently.

Next, FIGS. 11 and 12 show a second embodiment of the present invention. The feature of this embodiment is that guide means for guiding the mudguard cover to the left and right are provided on the track frame. The configuration is provided. Note that, in the present embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof will be omitted.

In the figure, reference numerals 41, 41,... Represent guide means provided between the track frame 7 and the mudguard cover 21 in place of the leaf spring 23 described in the first embodiment.
The guides 41 (only two are shown)
Is constituted by a guide plate 42 and a slide bar 43, and is disposed on both front and rear sides of the mudguard cover 21 with a space therebetween.

Here, the guide plate 42 is made of a rectangular plate material disposed in the left and right directions, and the lower end thereof straddles the upper plate portion 10A of the center frame 8 and the upper plate portion 11A of the side frame 11. Fixed by welding or the like. The guide plate 42 has a guide hole 42A formed of a long hole in the left-right direction.

The slide bar 43 is formed of a columnar body extending in the front and rear directions, and has its base end fixed to the front and rear ends of the mudguard cover 21 by welding or the like. The tip of the slide bar 43 is the guide plate 4.
The second guide hole 42A is slidably inserted in the left and right directions.

Thus, also in the present embodiment having the above-described configuration, it is possible to obtain substantially the same operation and effect as in the first embodiment. In particular, in the present embodiment, the slide bar 43 protruding from the mudguard cover 21 is attached to the track frame 7.
The guide plate 41 and the slide bar 43 guide the guide plate 41 so that the mudguard cover 21 can be stably supported on the track frame 7. At the same time, the vibration direction of the mudguard cover 21 can be regulated to the left and right, and the vibration operation of the mudguard cover 21 can be facilitated.

Next, FIGS. 13 to 18 show a third embodiment of the present invention.
This embodiment is characterized in that a vibration actuator that applies elliptical vibration to the mudguard cover is provided between the track frame and the mudguard cover. Note that, in the present embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof will be omitted.

In the drawing, reference numeral 51 denotes a mudguard cover used in the present embodiment. The mudguard cover 51 has substantially the same configuration as the mudguard cover 21 used in the first embodiment, and has an inner end 51A and an outer end 51A. 51B and the like. And
The mudguard cover 51 is arranged obliquely downward at an angle θ from the center frame 8 side to the side frame 11 side.

Reference numeral 52 denotes a support provided on the upper plate portion 10A of the center frame 8, and this support 52 supports a first hydraulic cylinder 53, which will be described later, with respect to the track frame 7 at an angle θ. Things.

Reference numeral 53 denotes the center frame 8 and the mudguard cover 5
1 is a first hydraulic cylinder as a first vibration actuator provided between the first hydraulic cylinder and the first hydraulic cylinder 53. The first hydraulic cylinder 53 is disposed at an angle θ corresponding to the mudguard cover 51, It is fixedly attached to the support 52 on the side of the center frame 8.

The first hydraulic cylinder 53 is provided in the
As shown in FIG. 4, bushes 5 serving as rod guides at both ends
4 and the tube 53A
A piston 53B slidably provided therein, a rod 53C whose base end is fixed to the piston 53A and protrudes from the tube 53A to the outside via a bush 54, and a rod 53C whose base end is fixed to the piston 53A and whose distal end is connected to the rod 53C. Is substantially constituted by another rod 53D extending in the opposite direction and inserted into the bush 54, and the inside of the tube 53A is defined by a piston 53B into two oil chambers 53E and 53F.

Then, the first hydraulic cylinder 53 expands and contracts the rod 53C by supplying and discharging pressurized oil to and from the oil chambers 53E and 53F via a first vibration control valve 59 described later.
A vibrating actuator for vibrating the mudguard cover 51 in an inclined direction (X-axis direction in FIG. 13) is configured.

Here, the first hydraulic cylinder 53 is operated for a time t.
And the stroke amount SX of the rod 53C is expressed by the following equation (1).
1 (see FIG. 16).

[0114]

SX = A1 × sin (ω × t−π / 2) Amplitude: A1 Angular velocity: ω

Numeral 55 denotes a first guide provided between the mudguard cover 51 and the first hydraulic cylinder 53. The first guide 55 is fixed to the tip of the rod 53C of the first hydraulic cylinder 53 as shown in FIG. Guide rail 55A,
A slider 55B is fixed along the end of the mudguard cover 51 and slidably fitted to the guide rail 55A.

Here, the guide rail 5 of the first guide 55
A substantially concave rail groove 55C is formed in 5A, and the slider 55B on the mudguard cover 51 side is fitted in the rail groove 55C in a state where it cannot be removed. The first guide 55 is configured to compensate for the relative displacement of the mudguard cover 51 relative to the first hydraulic cylinder 53 in the Y-axis direction.

56 is the center frame 8 and the mudguard cover 5
1 and a second hydraulic cylinder 56 as a second vibration actuator provided between the first hydraulic cylinder 53 and the second hydraulic cylinder 56. It is roughly constituted by a tube 56A provided on the plate portion 10A and a rod 56B provided in the tube 56A so as to be able to expand and contract via a piston (not shown).

The second hydraulic cylinder 56 expands and contracts the rod 56B by supplying and discharging pressure oil through a second vibration control valve 61, which will be described later, and moves the mudguard cover 51 in the thickness direction (FIG. 13). (A Y-axis direction in the middle).

Reference numeral 57 denotes a second guide provided between the mudguard cover 51 and the second hydraulic cylinder 56. The second guide 57 is substantially the same as the first guide 55 and has a rod 56B at the distal end of the second hydraulic cylinder 56. Guide rail 5 fixed to
7A and a slider 57B fixed to the back surface side of the mudguard cover 51 and slidably fitted to the guide rail 57A. The mudguard cover 51 is opposed to the second hydraulic cylinder 56 in the X-axis direction. It compensates for displacement.

Here, the second hydraulic cylinder 56 operates at time t.
And the stroke amount SY of the rod 56B is expressed by the following equation (1).
2 (see FIG. 17).

[0121]

SY = A2 × sin (ω × t−π) Amplitude: A2 Angular velocity: ω

That is, the second hydraulic cylinder 56 expands and contracts at the same angular velocity ω and the same frequency as the first hydraulic cylinder 53, and with a phase difference of about 90 degrees (π / 2) from the first hydraulic cylinder 53. Perform the operation.

Thus, the stroke amount SX of the first hydraulic cylinder 53 and the stroke amount SY of the second hydraulic cylinder 56
Is set to the relationship of the following Expression 13 by Expressions 11 and 12 (see FIG. 18).

[0124]

(Equation 13)

For this reason, the first hydraulic cylinder 53 and the second hydraulic cylinder 56 are configured to apply vibration having an elliptical motion to the mudguard cover 51 as described below.

In the above equation (13), the amplitude A1 in the X-axis direction is obtained.
Is equal to the amplitude A2 in the Y-axis direction, the vibration has a circular motion.

That is, the rod 53 of the first hydraulic cylinder 53
C extends from the minimum contraction position to the intermediate position, and the second
While the rod 56B of the hydraulic cylinder 56 is contracted from the intermediate position to the minimum contracted position (corresponding to the section b1 in FIGS. 16 and 17), the mudguard cover 51 holds the elliptical orbit 50 in FIG.
Out of the direction along the orbit curve 50A located in the third quadrant as indicated by the arrow.

The rod 53 of the first hydraulic cylinder 53
While C extends from the intermediate position to the maximum extension position and the rod 56B of the second hydraulic cylinder 56 extends from the minimum contraction position to the intermediate position (corresponding to the section b2 in FIGS. 16 and 17), the mudguard cover 51 Is the elliptical orbit 5 in FIG.
As shown by the arrow, it is displaced along the trajectory curve 50B located in the fourth quadrant of 0.

The rod 53 of the first hydraulic cylinder 53
While C decreases from the maximum extension position to the intermediate position, while the rod 56B of the second hydraulic cylinder 56 extends from the intermediate position to the maximum extension position (section b3 in FIGS. 16 and 17).
), The mudguard cover 51 is displaced as indicated by an arrow along a trajectory curve 50C located in the first quadrant of the elliptical trajectory 50 in FIG.

Furthermore, the rod 5 of the first hydraulic cylinder 53
While 3C is reduced from the intermediate position to the maximum reduction position, while the rod 56B of the second hydraulic cylinder 56 is reduced from the maximum extension position to the intermediate position (section b4 in FIGS. 16 and 17).
), The mudguard cover 51 is displaced as indicated by an arrow along a trajectory curve 50D located in the second quadrant of the elliptical trajectory 50 in FIG.

Next, a control circuit for controlling the operations of the first hydraulic cylinder 53 and the second hydraulic cylinder 56 will be described with reference to FIG.

In the figure, 58A and 58B respectively connect the oil chambers 53E and 53F of the first hydraulic cylinder 53 to the hydraulic pump 25,
A pair of pipes 59 connected to the tank 26 is a first vibration control valve provided in the middle of these pipes 58A and 58B. The first vibration control valve 59 is used in the first embodiment. For example, in the same manner as the vibration control valve 28 described in
It is constituted by a position or 4-port 2-position electromagnetic directional control valve.

The first vibration control valve 59 is continuously switched by outputting a control signal from a signal generator 62 to be described later, and the first hydraulic cylinder 53 is controlled in accordance with this cycle. Is repeatedly operated to extend and contract.

Reference numerals 60A and 60B denote a pair of conduits connecting the second hydraulic cylinder 56 to the hydraulic pump 25 and the tank 26;
Reference numeral 1 denotes a second vibration control valve provided in the middle of these conduits 60A and 60B. The second vibration control valve 61 is configured in substantially the same manner as the first vibration control valve 59. The switching is continuously controlled by outputting the control signal from the signal generator 62, and the rod 56B of the second hydraulic cylinder 56 is repeatedly extended and contracted in accordance with this cycle.

Reference numeral 62 denotes a signal generator for the first vibration control valve 59 and the second vibration control valve 61.
Outputs, for example, a control signal having a frequency corresponding to the vibration characteristic of Formula 11 to the first vibration control valve 59 via the amplifier 63, and outputs the control signal to the second vibration control via the delay device 64. It is also output to the application control 61.

Here, the delay device 64 is connected to the signal generator 62
Is output to the second vibration control valve 61 with a phase difference of about 90 degrees (π / 2). Therefore, a control signal having a frequency corresponding to the vibration characteristic of Equation 12 is output to the second excitation control valve 61.

As described above, the output signal from the signal generator 62 is output to the first vibration control valve 59 and the second vibration control valve 61, respectively, and the control valves 59 and 61 are switched to control. , The first hydraulic cylinder 53 and the second hydraulic cylinder 56 expand and contract with vibration characteristics of Equations 11 and 12, respectively.

Thus, in the present embodiment configured as described above, the first hydraulic cylinder 53 and the second hydraulic cylinder 5
6, the vibration that gives an elliptical motion to the mudguard cover 51 is added. Therefore, the mud on the mudguard cover 51 is inclined in two directions, that is, an inclined direction and a direction perpendicular to the inclined direction (plate thickness direction). An inertia force can be added, and substantially the same operation and effect as in the first embodiment can be obtained.

In particular, in the present embodiment, since the mudguard cover 51 can be positively vibrated in the thickness direction by the second hydraulic cylinder 56, a greater inertia force is applied to the mud on the mudguard cover 51. And the mud discharge efficiency can be further improved.

Next, FIGS. 19 to 24 show a fourth embodiment of the present invention.
The feature of this embodiment is that the hydraulic cylinder vibrates only in the inclined direction with respect to the mudguard cover, and the supply / discharge direction of the pressure oil to / from this hydraulic cylinder is switched using an electromagnetic valve. By outputting a control signal having a sawtooth waveform to the solenoid valve, the hydraulic cylinder is driven faster on one side of the vibration direction and slower on the other side. Note that, in the present embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof will be omitted.

In the drawing, reference numeral 71 denotes a mudguard cover used in the present embodiment. The mudguard cover 71 is also similar to the mudguard cover 21 according to the first embodiment, and has an inner end 71A, an outer end 71B and an inner end 71A. Has a notch 71C,
The outer end 71B is connected to the upper plate 11A of the side frame 11.
A folded portion 71D is formed at a position on the corner of the corner with the side plate portion 11C and bent downward in a substantially L-shape. And this mudguard cover 71 is arranged diagonally left and right,
A coating layer (not shown) is formed on the surface.

Are guides disposed between the upper plate portion 11A of the side frame 11 and the mudguard cover 71. The guides 72 are also the second guides described in the third embodiment. Almost like 57, side frame 1
A guide rail 72A on one side and a slider 72B on the mudguard cover 71 side make it possible for the mudguard cover 71 to slide and displace in the inclined direction in the directions indicated by arrows b and b 'in FIGS. Compensated.

Are hydraulic cylinders as vibrating actuators used in the present embodiment. The hydraulic cylinder 73 includes a tube 73A provided on the upper plate portion 10A of the center frame 8 and a tube 73A. A piston 73B (see FIG. 22) provided therein and a rod 73C whose base end is attached to the piston 73B and whose tip end is swingably provided on the mudguard cover 71. Two oil chambers 73D and 73E are defined.

The hydraulic cylinder 73 is supplied with hydraulic oil from the hydraulic pump 25 to the oil chambers 73D and 73E via the solenoid valve 75 as described later.
0, the driving speed is high when driving in one direction of the vibration direction in the direction of arrow b in FIG. 21, and the driving is slow when driving the other side in the vibration direction in the direction of arrow b '.

Next, referring to FIG.
A control circuit for controlling the operation of the device will be described.

In the figure, 74A and 74B are hydraulic cylinders 73.
A pair of pipelines 75 for connecting the oil chambers 73D and 73E to the hydraulic pump 25 and the tank 26, and 75 are these pipelines 74A and 74.
B, which is provided in the middle of B and serves as a vibration control valve which constitutes an actuator control means together with a signal generator 76 described later. This electromagnetic valve 75 is also used for the vibration control described in the first embodiment. The control valve 28 is configured in the same manner as a solenoid valve of, for example, a 4-port 2-position, almost similarly to the control valve 28.

The electromagnetic valve 75 is connected to the signal generator 7
6 is output to the electromagnetic pilot section 75A, the switching is continuously controlled between the switching position (c) and the switching position (d), and the hydraulic cylinder 73 is controlled in accordance with this cycle.
Is repeatedly extended and contracted.

Reference numeral 76 denotes a signal generator serving as a signal output means for the solenoid valve 75. The signal generator 76 generates a current, voltage, or the like having a saw-tooth waveform with respect to time t as shown in FIG. The switching control of the solenoid valve 75 is performed by outputting a control signal to the solenoid valve 75. As a result, as is clear from the inclinations of the straight lines L and L 'shown in FIG. 24, the rod 73C of the hydraulic cylinder 73 is displaced faster when extended and slower when contracted.

Thus, in the present embodiment configured as described above, when the mud 30 falls on the mudguard cover 71, the electromagnetic valve 75 controls the expansion / contraction operation of the hydraulic cylinder 73, thereby causing the mudguard cover 71 to move in the arrow direction. It is possible to increase the inertia force applied to the mud 30 in the direction of arrow b 'by rapidly displacing in the direction of arrow b. Thereby, the mud 30 can be separated from the mudguard cover 71 and can be smoothly discharged in the inclination direction of the mudguard cover 71.

Further, the mudguard cover 71 is displaced slowly in the direction of arrow b 'to reduce the inertial force applied to the mud 30 in the direction of arrow b, whereby the mud 30 is moved in the direction of arrow Fb. It is possible to hold the mudguard cover 71 on the mudguard cover 71 without sliding.

Therefore, according to the present embodiment, substantially the same functions and effects as those of the first embodiment can be obtained. In addition, the mudguard 30 is vibrated by the hydraulic cylinder 73 to thereby reduce the mud 30. Left in the direction of arrow Fb ',
It can be gradually slid to the right outside and can be discharged from the mudguard cover 71, and the discharge efficiency of the mud 30 can be increased.

Next, FIGS. 25 to 27 show a fifth embodiment of the present invention. The feature of this embodiment is that a hydraulic cylinder vibrates a mudguard cover only in an inclined direction, A slow return valve that switches the direction of supply and discharge of pressure oil to and from the cylinder using an electromagnetic valve, and throttles the pressure oil discharged from the hydraulic cylinder in the middle of the pipeline connecting the hydraulic cylinder to the hydraulic source. Is provided.

In this embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof will be omitted.

In the drawing, reference numeral 81 denotes a mudguard cover used in the present embodiment. This mudguard cover 81 is also configured substantially in the same manner as the mudguard cover 71 according to the fourth embodiment, and is disposed diagonally left and right. Is what is done.

Reference numeral 82 denotes a hydraulic cylinder as a vibration actuator used in the present embodiment.
2, the hydraulic cylinder 7 according to the fourth embodiment is also used.
In substantially the same manner as in 3, the tube 82A is constituted by a piston 82B and a rod 82C, and the inside of the tube 82A is defined by a piston 82B into two oil chambers 82D and 82E.

A pair of pipes 83A and 83B connect the oil chambers 82D and 82E of the hydraulic cylinder 82 to the hydraulic pump 25 and the tank 26, and a pipe 84 is provided in the middle of these pipes 83A and 83B to generate a signal to be described later. The electromagnetic valve 84 is an electromagnetic control valve that constitutes an actuator control means together with the actuator 85. This electromagnetic valve 84 is also, for example, a four-port two-way valve in substantially the same manner as the vibration control valve 28 described in the first embodiment. It is configured as a position solenoid valve.

The solenoid valve 84 is connected to the signal generator 8
5, when the control signal is output to the electromagnetic pilot section 84A, the switching is continuously controlled between the switching position (c) and the switching position (d).

Reference numeral 85 denotes a signal generator for the solenoid valve 84.
The signal generator 85 outputs a control signal such as a current or a voltage having a pulse-like waveform with respect to time t to the solenoid valve 84 as shown in FIG. 26, for example, and performs switching control of the solenoid valve 84. Things.

Here, as shown in FIG.
5 outputs the negative control signal (-V) to the solenoid valve 84 at time t1 to switch the solenoid valve 84 to the switching position (d) and to change the positive control signal (V) from the time t1. The solenoid valve 84 is switched to the switching position (C) by outputting to the solenoid valve 84 with a long time t2 (t2> t1).

Incidentally, the pressure oil from the hydraulic pump 25 will be described later.
Check valve 86A of slow return valve 86
The flow rate when passing in the direction indicated by the arrow q1 shown in FIG.
(M ^Three / Sec), and the pressure oil from the hydraulic cylinder 82
The throttle 86B of the slow return valve 86 is shown in FIG.
The flow rate when passing in the direction of arrow q2 is expressed as Q2 (m^Three / S
ec), the times t1 and t2 are given by
It is desirable to set the relationship.

[0161]

[Equation 14] Q1 × t1 = Q2 × t2

Reference numeral 86 denotes a slow return valve provided in the middle of a pipe 83B connecting the oil chamber 82E of the hydraulic cylinder 82 to the hydraulic pump 25.
Reference numeral 6 includes a check valve 86A and a throttle 86B.

Here, the check valve 86A is connected to the solenoid valve 84.
Is switched to the switching position (d), the hydraulic pump 2
5 allows the pressure oil from 5 to flow to the oil chamber 82E side of the hydraulic cylinder 82, and shuts off the reverse flow. The throttle 86B is configured to apply a throttle function to the pressure oil flowing from the oil chamber 82E to the tank 26 when the solenoid valve 84 is switched to the switching position (C).

Therefore, when the electromagnetic valve 84 is switched to the switching position (d) by the signal generator 85, the pressure oil from the hydraulic pump 25 is supplied to the hydraulic cylinder 82 via the check valve 86A of the slow return valve 86. While being supplied to the chamber 82E, the pressure oil in the oil chamber 82D is returned to the tank 26, and the rod 82C is displaced in the extending direction.

When the solenoid valve 84 is switched to the switching position (C), the pressure oil from the hydraulic pump 25 is supplied into the oil chamber 82D of the hydraulic cylinder 82 and the oil chamber 8
The pressure oil of 2E is returned to the tank 26 through the throttle 86B, and the rod 82C is displaced in the contracting direction. As a result, the rod 82C of the hydraulic cylinder 82 is rapidly displaced when extended, and displaced slowly when contracted, as indicated by the characteristic line shown in FIG.

Thus, in the present embodiment configured as described above, substantially the same operation and effect as those of the fourth embodiment can be obtained.

Next, FIGS. 28 to 30 show a sixth embodiment of the present invention.
The feature of this embodiment is that a hydraulic cylinder vibrates only in an inclined direction with respect to a mudguard cover, and a solenoid valve that controls the supply / discharge direction of pressure oil to / from the hydraulic cylinder is a hydraulic valve. A first switching position for supplying pressure oil to the oil chamber having the smaller pressure receiving area of the two oil chambers defined in the cylinder, and a second switching position for supplying pressure oil to both oil chambers. That is, the structure is selectively switched.

In the present embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof will be omitted.

In the figure, reference numeral 91 denotes a mudguard cover used in the present embodiment. This mudguard cover 91 is also constructed in substantially the same manner as the mudguard cover 71 according to the fourth embodiment, and is disposed diagonally left and right. Is what is done.

Reference numeral 92 denotes a hydraulic cylinder as a vibration actuator used in the present embodiment.
2, the hydraulic cylinder 7 according to the fourth embodiment is also used.
3, the tube 92A and the tube 92A.
A, a large-diameter rod 92C whose base end is fixed to the piston 92B and whose distal end projects out of the tube 92A and is connected to the mudguard cover 91.
And a small-diameter rod 92D whose base end is fixed to the piston 92B and whose distal end projects out of the tube 92A in a direction opposite to the large-diameter rod 92C.

Further, a piston 92B is provided in the tube 92A.
The piston 92B has different pressure receiving areas S1 and S2 with respect to the oil chambers 92E and 92F, respectively. Here, the larger the pressure receiving area of the piston 92B, the lower the speed of the piston 92B.
1, S2 is set in the relationship of the following equation (15).

[0172]

## EQU15 ## 0 <(S1-S2) <S2

For this reason, when the solenoid valve 94 is switched to the switching position (C), the hydraulic cylinder 92 supplies the pressure oil from the hydraulic pump 25 only to the oil chamber 92F and the oil chamber 92E The large-diameter rod 92C is configured to be displaced slowly in the reduction direction on the tank 26 side. When the solenoid valve 94 is switched to the switching position (d), the hydraulic cylinder 92 supplies the hydraulic oil from the hydraulic pump 25 to both the oil chambers 92E and 92F via the solenoid valve 94, and the large-diameter rod 92C is configured to be rapidly displaced in the extension direction.

Reference numerals 93A and 93B denote a pair of conduits for connecting the oil chambers 92E and 92F of the hydraulic cylinder 92 to the hydraulic pump 25 and the tank 26, and reference numeral 94 denotes a conduit provided along the conduit 93A. An electromagnetic valve as a vibration control valve constituting the control means.
Is configured, for example, as a three-port, two-position solenoid valve, in substantially the same manner as the vibration control valve 28 described in the first embodiment.

The solenoid valve 94 is connected to the signal generator 9
When the control signal is output to the electromagnetic pilot section 94A, the switching control is continuously performed between the first switching position (c) and the second switching position (d).

Here, when the solenoid valve 94 is switched to the first switching position (C), the pressure oil from the hydraulic pump 25 is supplied to the oil chambers 92E and 92F of the hydraulic cylinder 92 which have the smaller pressure receiving area S2. The oil chamber 92E, which is supplied only to the oil chamber 92F and has a larger pressure receiving area S1, is connected to the tank 26 side. When the solenoid valve 94 is switched to the second switching position (d), the pipe 95 on the oil chamber 92F side communicates with the oil chamber 92E, and the pressure oil from the hydraulic pump 25 is supplied to both the hydraulic cylinder 92. The oil is supplied to the oil chambers 92E and 92F.

Reference numeral 96 denotes a signal generator for the solenoid valve 94.
As with the signal generator 85 according to the fifth embodiment, a control signal such as a current or voltage having a pulse-like waveform with respect to time t is also applied to the signal generator 96, as shown in FIG. This is output to the solenoid valve 94 to control the switching of the solenoid valve 94.

Here, as shown in FIG.
6 switches the solenoid valve 94 to the second switching position (d) by outputting a negative control signal (-V ') to the solenoid valve 94 at time t1', and simultaneously outputs the positive control signal (V ').
To a time t2 '(t2'> t longer than the time t1 ').
By outputting 1 ') to the solenoid valve 94, the solenoid valve 94 is switched to the first switching position (c).

It is preferable that the times t1 'and t2' be set in relation to the pressure receiving areas S1 and S2 of the hydraulic cylinder 92 in the following equation (20).

Here, the times t1 'and t2' and the pressure receiving area S
To explain the relationship between the hydraulic cylinder 92 and the hydraulic cylinder 92, first, assuming that the displacement speed of the large-diameter rod 92C of the hydraulic cylinder 92 at the time of contraction is v1, the supply amount Q1 'of the hydraulic oil to the hydraulic cylinder 92 is

[0181]

## EQU16 ## Q1 '= S2.times.v1.

The large-diameter rod 92 of the hydraulic cylinder 92
Assuming that the displacement speed at the time of extension of C is v2, the supply amount Q2 'of pressure oil to the hydraulic cylinder 92 is

[0183]

## EQU17 ## Q2 '= (S1-S2) .times.v2.

Since the supply amount Q1 'at the time of expansion and the supply amount Q2' at the time of contraction are equal (Q1 '= Q2'),

[0185]

S2 × v1 = (S1−S2) × v2

On the other hand, the displacement amount of the large-diameter rod 92C when extended and the displacement amount when contracted are equal.

[0187]

## EQU19 ## v2.times.t1 '= v1.times.t2'.

[0188]

## EQU20 ## t2 '/ t1' = S2 / (S1-S2) holds.

Thus, in the present embodiment configured as above, when the electromagnetic valve 94 is switched to the switching position (C) by the signal generator 96, the hydraulic oil from the hydraulic pump 25 is applied to the hydraulic cylinder 92. The large-diameter rod 92C is supplied to the oil chamber 92F and can be displaced in the contracting direction by the pressure receiving area S2. When the solenoid valve 94 is switched to the switching position (d), the pressure oil from the hydraulic pump 25 is supplied to both the oil chambers 92E and 92F of the hydraulic cylinder 92, and the difference between the pressure receiving areas S1 and S2 ( By S1 -S2), the large-diameter rod 92C can be displaced in the extension direction.

Therefore, according to the present embodiment, since the pressure receiving areas S2 and S1 of the hydraulic cylinder 92 are set in the relationship of the following equation (15), the large-diameter rod 92C of the hydraulic cylinder 92 is connected to the characteristic line shown in FIG. As described above, the displacement can be made faster at the time of extension, and the displacement can be made later at the time of contraction, so that substantially the same operation and effect as in the fourth embodiment can be obtained.

Next, FIG. 31 shows a seventh embodiment of the present invention. The feature of this embodiment is that a mudguard cover 101 is provided instead of the mudguard cover 21 according to the first embodiment, and this mudguard is provided. The cover 101 is divided into two cover members 102 and 103 in the front and rear directions.
2 and 103 are integrally connected using a plurality of bolts 104 serving as connecting tools. Note that, in the present embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof will be omitted.

Here, the cover 1 of the mudguard cover 101
Numeral 02 is a plate-like body elongated in the front and rear directions, and has an outer end 102A, an inner end 102B, and a notch 102.
C. The cover body 103 is formed of a substantially trapezoidal plate-like body, and has an outer end 103A and an inner end 10A.
3B. Then, the mudguard cover 101 is placed above the inner end 102B of the cover body 102.
The outer ends 103A of the third cover 3 are overlapped with each other, and in this state, the covers 102 and 103 are fastened by bolts 104 or the like.

Therefore, the present embodiment having the above-described structure can provide substantially the same operation and effect as those of the first embodiment. Particularly, in the present embodiment, the mudguard cover 101 is divided into two cover bodies 102 and 103 in the front and rear directions. Therefore, when attaching and removing the mudguard cover 101, the cover bodies 102 and 103 are separated from the track frame. 7 can be separately attached to and detached from each other, so that work can be performed easily, and workability and the like can be improved.

Next, FIGS. 32 and 33 show an eighth embodiment of the present invention. The feature of this embodiment is that the mudguard cover 11 is replaced with the mudguard cover 71 according to the fourth embodiment.
1 and the mudguard cover 111 is located in front, rear and left,
Four cover bodies 112, 113, 1 divided in the right direction
14, 115, and these cover bodies 112
Reference numerals 115 are used to integrally connect the front, rear, left, and right hinges 116 and the like as connecting tools, and guide the mudguard cover 111 to the left and right sides of the upper plate 11A of the side frame 11 so as to be slidable left and right. The sliding members 117 and 118 are provided. In this embodiment, the same components as those in the fourth embodiment are denoted by the same reference numerals, and the description thereof will be omitted.

Here, the sliding members 117 and 118 are formed in a square plate shape from a hard and highly wear-resistant material such as ceramics, and the sliding member 117 is provided on the side frame 11 and slides. The moving member 118 is provided on the lower surface side of the mudguard cover 111. And the sliding member 1
Reference numerals 17 and 118 make sliding contact with each other, and support the mudguard cover 111 to vibrate in the inclined direction from below.

Therefore, also in the present embodiment having such a configuration, it is possible to obtain substantially the same operation and effect as in the fourth embodiment. In particular, in the present embodiment, since the mudguard cover 111 is divided into cover bodies 112 to 115 and these are connected using the hinge 116, for example, even when mud is deposited between the track frame 7 and the mudguard cover 111, For example, the cover bodies 112 and 113 are
4 and 115, centering on the front and rear hinges 116
2. By turning left and right in the directions indicated by the arrows shown in FIG. 33, the mud removal operation can be easily performed in this state, and the operation efficiency can be improved. In this case, for example, the cover bodies 112 and 114 may be rotated forward and backward about the left and right hinges 116 with respect to the cover bodies 113 and 115.

Further, the mudguard cover 111 is attached to the sliding member 11.
Since the configuration is such that the mudguard cover 71 is supported by the side frame 11 with the use of the guides 72 and the like, the mudguard cover 71 does not need to be attached to the side frame 11 using the guide 72 or the like as described in the fourth embodiment. Can be easily attached and detached.

Next, FIG. 34 shows a ninth embodiment of the present invention. This embodiment is characterized in that a vibration control valve such as a solenoid valve is used as in the above-described embodiments. Instead of driving the hydraulic cylinder, the hydraulic cylinder is driven by using a hydraulic pilot type switching valve using self-pressure. Note that, in the present embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof will be omitted.

In the figure, reference numeral 121 denotes a mudguard cover according to the present embodiment. This mudguard cover 121 has substantially the same configuration as the mudguard cover 71 according to the fourth embodiment, and is disposed diagonally left and right. Have been.

Reference numeral 122 denotes a hydraulic cylinder as a vibration actuator used in the present embodiment. The hydraulic cylinder 122 is the hydraulic cylinder 92 described in the sixth embodiment.
And the tube 122A, the piston 122B,
It is roughly constituted by a large-diameter rod 122C and a small-diameter rod 122D. Further, the interior of the tube 122A is made up of two oil chambers 122E, 122E by a piston 122B.
2F, the piston 122B is connected to these oil chambers 1
Pressure receiving areas S1 and S2 of different sizes are provided for 22E and 122F, respectively.

Therefore, similarly to the hydraulic cylinder 92 according to the sixth embodiment, the hydraulic cylinder 122 supplies the pressure oil from the hydraulic pump 25 to the oil chamber 122F of the oil chambers 122E and 122F having the smaller pressure receiving area S2. The large-diameter rod 122C is displaced slowly in the contraction direction when the pressure oil is supplied from the hydraulic pump 25 to both the oil chambers 122E and 122F. It has become.

Reference numeral 123 denotes a pump-side pipe 123 having one end connected to the oil chamber 122F of the hydraulic cylinder 122 and the other end connected to the hydraulic pump 25. A switching valve 29 is provided in the middle of the pipe 123. Have been.

Reference numeral 124 denotes a port-side pipe connected at one end to the oil chamber 122F of the hydraulic cylinder 122 together with the pipe 123, and the other end to a port of a switching valve 126 described later. Oil chamber 122
E shows a tank-side conduit connected to the tank 26 at the other end.

Reference numeral 126 denotes a three-port, two-position hydraulic pilot type switching valve serving as a vibration control valve constituting an actuator control means together with a control valve 129 described later.
26 indicates that the pressure oil from the pipe 124 is
And the like, and a large hydraulic pilot unit 126B in which the control valve 129 supplies hydraulic oil from the hydraulic pump 25 as pilot pressure through the pilot line 128 and the like.
And the pressure receiving area of the large hydraulic pilot portion 126B is larger than the pressure receiving area of the small hydraulic pilot portion 126A.

Therefore, when the pilot pressure is supplied only to the small hydraulic pilot portion 126A, the switching valve 126 holds the first switching position (C), and the small hydraulic pilot portion 1
When the pilot pressure is simultaneously supplied to 26A and the large hydraulic pilot portion 126B, the switch is switched to the second switching position (d).

When the switching valve 126 holds the switching position (C), the pressure oil from the hydraulic pump 25 is supplied to the oil chamber 12 having the smaller pressure receiving area S2 of the hydraulic cylinder 122.
2F, the oil chamber 122 having the larger pressure receiving area S1
When the pressure oil is discharged from E, the large-diameter rod 122
C is displaced slowly in the reduction direction. On the other hand, when the switching valve 126 is switched to the switching position (d), the hydraulic pump 25
Is supplied to both oil chambers 122E and 122F, and the difference between the pressure receiving areas S1 and S2 causes the large-diameter rod 122
C is rapidly displaced in the extension direction.

129 is a piston 1 of the hydraulic cylinder 122
The control valve operates in conjunction with the control valve 229B.
Is a piston 122B that reciprocates in the tube 122A.
By switching the pilot pressure from the hydraulic pump 25 to the large hydraulic pilot portion 126B of the switching valve 126 in accordance with the position of the switching valve 126, the switching valve 126 is switched between the first switching position (c) and the second switching position (d). ).

Here, the control valve 129 is connected to the hydraulic cylinder 1
22 is connected to a piston 122B via a small-diameter rod 122D. When the piston 122B reaches a prescribed position (for example, a stroke end) on the side of the oil chamber 122F, the piston 122B is switched to the control position (e) and branched from the oil passage 125. The branched pipeline 130 and the pilot pipeline 128 communicate with each other. As a result, the pilot pressure from the hydraulic pump 25 changes to the switching valve 1
The switching valve 127 is supplied to only the small hydraulic pilot portion 126A, and the switching valve 127 is switched to the first switching position (C).

On the other hand, the control valve 129 is
When the second piston 122B reaches a specified position (for example, a stroke end) on the oil chamber 122E side, it is switched to the control position (F), and the branch line 1 branched from the line 123
31 and the pilot line 128 are communicated. As a result, the pilot pressure from the hydraulic pump 25 is
Small hydraulic pilot unit 126A and large hydraulic pilot unit 1
26B, and the switching valve 126 switches to the second switching position (d).

Thus, in the present embodiment configured as described above, when the switching valve 126 is at the first switching position (C) as shown in FIG. 34, the hydraulic oil from the hydraulic pump 25 is supplied to the hydraulic cylinder. The oil is supplied to the oil chamber 122F and the oil is discharged from the oil chamber 122E.
2C displaces slowly in the reduction direction. And the piston 12
When 2B reaches the stroke end on the reduction side, the control valve 1
29 is switched from the control position (e) to (f), and following this, the switching valve 126 is switched from the switching position (c) to (d), so that the large-diameter rod 122C is rapidly displaced in the extension direction.

When the piston 122B reaches the stroke end on the extension side, the control valve 129 is switched from the control position (f) to (e), and the switching valve 126 is switched from the switching position (d) to (c). Large diameter rod 1
22C is displaced again in the reduction direction. As described above, the hydraulic cylinder 122 is configured such that the piston 122B performs self-excited vibration when the switching valve 126 and the control valve 129 are switched.

Therefore, also in the present embodiment, the hydraulic cylinder 122 can displace the large-diameter rod 122C slowly in the contracting direction and quickly displace the large-diameter rod 122C in the extending direction, and the operation is substantially the same as that of the fourth embodiment. The effect can be obtained.

Next, FIGS. 35 and 36 show a tenth embodiment of the present invention. In the present embodiment, the same components as those in the fourth embodiment are designated by the same reference numerals. , The description of which will be omitted.

However, the feature of the present embodiment is that the hydraulic cylinder 141, which is the vibration actuator, is separated from the mudguard cover 142 at a position outside and forward of the mudguard cover 142 and is disposed on the leg 10 of the center frame 8. I did it.

Here, the hydraulic cylinder 141 is substantially the same as the hydraulic cylinder 73 according to the fourth embodiment, and is a tube 141A provided on the leg 10 of the center frame 8.
And a rod 141B whose tip end side is swingably provided on the mudguard cover 142.

However, this hydraulic cylinder 141 connects the rod 141B to the side frame 11 from the tube 141A.
To the side, it projects in a direction opposite to the hydraulic cylinder 73 according to the fourth embodiment. And the hydraulic cylinder 141
For example, by using the solenoid valve 75 and the signal generator 76 according to the fourth embodiment, the rod 73C is displaced quickly when contracted, and displaced slowly when extended.

Thus, also in the present embodiment configured as described above, it is possible to obtain substantially the same operation and effect as in the fourth embodiment.

The sixth embodiment has exemplified the case where the large-diameter rod 92C of the hydraulic cylinder 92 is projected from the tube 92A toward the side frame 11.
Instead, for example, similarly to the tenth embodiment, the large-diameter rod 92C is moved from the tube 92A to the center frame 8.
It may be configured to protrude toward the center side (toward the round body 9) of the. In this case, by setting the pressure receiving areas S1 and S2 of the piston 92B in the following relationship, the large-diameter rod 92C can be quickly displaced in the contracting direction and slowly displaced in the extending direction.

[0219]

(S1−S2)> S2

Further, in the first embodiment, the case where the hydraulic cylinder 24 is driven by using the vibration control valve 28 composed of an electromagnetic valve or the like is exemplified. However, instead of this, for example, the ninth embodiment is used. As described above, the hydraulic cylinder may be driven by using a hydraulic pilot switching valve using self-pressure. This is the same for the second, third, fourth, fifth, sixth, seventh, eighth, and tenth embodiments.

Further, in the fourth embodiment, the tube 73A of the hydraulic cylinder 73 is moved downward (to the side frame 11).
Side) and a rod 73C with respect to the tube 73A.
Is placed on the upper side (center frame 8 side), and the rod 73C
The tube 73A is configured to be rapidly displaced when it is extended and displaced slowly when it is contracted.
The lower direction may be reversed. Also in this case, the rod 73C may be displaced quickly when the rod 73C contracts, and may be displaced slowly when the rod 73C extends. This is the same for the fifth, sixth, seventh, eighth, and ninth embodiments.

Further, in each of the embodiments, the description has been made assuming that a coating layer made of a water-repellent film is formed on the surface side of the mudguard cover by means of coating or the like. Alternatively, for example, ethylene tetrafluoride or the like may be used. It is good also as a structure which sticks the resinous sheet which consists of on the surface of a mudguard cover.

Furthermore, in each of the embodiments, a description has been given of a hydraulic excavator as an example of a tracked vehicle, but the present invention is not limited to this, and is widely applied to other tracked vehicles such as a hydraulic crane and a bulldozer. Applicable.

[0224]

As described in detail above, according to the first aspect of the present invention, the mudguard cover is disposed obliquely downward and leftward and rightward from the center frame to the side frame side. Is vibrated in the left and right horizontal directions using the vibration actuator, so that when the mud falls and adheres to the mudguard cover, the mudguard cover can be vibrated by the vibration actuator. Inertia can be imparted to the mud in the thickness direction in addition to the inclination direction of the mudguard cover, and the inertia force in the thickness direction allows the mud to be efficiently separated from the mudguard cover, and the mud along the inclination direction of the mudguard cover. It can be discharged smoothly.

As a result, it is possible to prevent the mud scraped up by the crawler belt from accumulating on the track frame during traveling, and to simplify the mud removing operation at the time of maintenance of the vehicle, thereby improving workability and the like. be able to.

According to the invention of claim 2, since the vibrating actuator is constituted by a hydraulic cylinder which repeatedly expands and contracts in the left and right horizontal directions, the rod is repeatedly supplied and discharged from the outside into the tube by connecting and disconnecting the rod. The mudguard cover can be vibrated at a high speed in accordance with the telescopic operation.

According to the third aspect of the present invention, the mudguard cover is disposed obliquely downward and leftward and rightward from the center frame to the side frame, and the mudguard cover is first and second vibrating. When the mud falls onto the mudguard cover, the first and second vibrating actuators are activated by vibrating in two directions, a tilt direction and a direction different from the tilt direction, by using the actuator for vibration. In addition to the inertial force in the inclined direction to the mud on the mudguard cover, an inertial force in a direction different from the inclined direction can be positively added to the mud, so that the mud discharge efficiency can be further enhanced.

Further, in the invention according to claim 4, since the first and second vibrating actuators are configured to add a vibration giving a circular motion or an elliptical motion to the mudguard cover, the mudguard cover is mounted on the track frame. Can be repeatedly vibrated so as to draw a circular or elliptical locus, and the mud can be discharged more efficiently.

Further, the first vibrating actuator is vibrated in the direction in which the mudguard cover is inclined, and the second vibrating actuator is 90 degrees apart from the first vibrating actuator. By vibrating the inclined cover in the inclination direction and the plate thickness direction with a phase difference, a circular or elliptical vibration can be stably added to the mudguard cover.

On the other hand, according to the sixth aspect of the present invention, the vibrating actuator is driven faster by one side of the vibration direction and slower by the other side by the actuator control means, so that the mudguard cover is vibrated by the vibrating actuator. By changing the inertia force applied to the mud between one side and the other side in the vibration direction, the mud can be efficiently separated from the mudguard cover, and even in this case, almost the same as the invention of claim 1 The mud discharge efficiency can be improved.

Further, according to the seventh aspect of the present invention, the mudguard cover is controlled only when the mudguard cover is displaced from the side frame toward the center frame by controlling the supply and discharge of the pressure oil to and from the vibration actuator by the actuator control means. The high-speed drive makes it possible to apply a large inertial force to the mud when the mudguard cover is displaced from the side frame to the center frame, and the mud can be separated from the mudguard cover and discharged smoothly. it can.

In this case, by disposing the mudguard cover obliquely downward and leftward and rightward from the center frame to the side frame side as in the invention of claim 8, the mud is prevented from being inclined in the inclination direction of the mudguard cover. It becomes possible to discharge more smoothly along.

Further, according to the ninth aspect of the present invention, the actuator control means switches a supply / discharge direction of the pressure oil to / from the vibration actuator in response to a control signal from the outside, Signal control means for outputting the control signal to the control valve as a signal having a saw-tooth waveform, so that the vibration control valve is switched substantially in accordance with the waveform of the control signal. The vibration actuator can be moved quickly on one side of the left and right sides and slowly on the other side, and the performance and reliability of the actuator control means can be improved.

Further, as in the tenth aspect of the present invention, the actuator control means includes a vibration control valve for switching the direction of supply and discharge of the pressure oil to and from the vibration actuator, and a mudguard cover for controlling the vibration direction by the vibration actuator. The performance, reliability, etc. of the actuator control means can be improved even with a slow return valve which exerts a throttling action on the pressure oil discharged from the vibration actuator when displaced to one side. Can be increased almost as well.

Further, as in the eleventh aspect of the present invention, the vibrating actuator is constituted by a hydraulic cylinder having two oil chambers having different pressure receiving areas from each other, and the actuator control means controls the hydraulic cylinder by the two hydraulic cylinders. A first switching position for supplying the pressure oil to the oil chamber having the smaller pressure receiving area of the oil chamber and discharging the pressure oil from the larger oil chamber, and supplying the pressure oil to both the oil chambers. Even in the case of using a vibration control valve that can be selectively switched to the second switching position, the performance and reliability of the actuator control means can be improved almost in the same manner as in the seventh aspect.

According to the twelfth aspect of the present invention, since the water repellent film is formed on the surface of the mudguard cover, the water repellent film can prevent mud and the like from adhering to the surface of the mudguard cover. The mud can be quickly discharged to the outside by the vibration of the mud cover.

Further, according to the thirteenth aspect of the present invention, the mudguard cover is divided into a plurality of sheets in the front and rear directions or left and right directions.
Since each of these covers is configured to be integrally connected to each other using a connecting tool, for example, when attaching a mudguard cover, each cover is separately attached to the track frame in advance, and in this state, each cover is connected using the connecting tool. By being integrally connected to each other, the work of attaching the mudguard cover can be easily performed, and the workability and the like can be improved.

[Brief description of the drawings]

FIG. 1 is a front view showing a hydraulic excavator applied to a first embodiment of the present invention.

FIG. 2 is an enlarged plan view showing a track frame, a mudguard cover, a hydraulic cylinder, and the like in FIG. 1;

FIG. 3 is a perspective view showing a track frame, a mudguard cover, and the like in FIG. 2 with a hydraulic cylinder removed.

FIG. 4 is an enlarged cross-sectional view as seen from a direction indicated by arrows IV-IV in FIG. 2;

FIG. 5 is an enlarged sectional view of a main part showing a mudguard cover, a hydraulic cylinder and the like in FIG. 4;

FIG. 6 is a hydraulic circuit diagram for driving the hydraulic cylinder according to the first embodiment.

FIG. 7 is a cross-sectional view showing the direction of the inertial force acting on the mud when the vibration acceleration of the mudguard cover is positive, as viewed from the same position as in FIG. 5;

FIG. 8 is a cross-sectional view showing the direction of the inertial force acting on the mud when the vibration acceleration of the mudguard cover is negative as viewed from the same position as in FIG. 5;

FIG. 9 is a characteristic diagram illustrating a relationship between a stroke amount of a hydraulic cylinder and time.

FIG. 10 is a characteristic diagram showing a relationship between vibration acceleration of a hydraulic cylinder and time.

FIG. 11 is an enlarged partial plan view showing a track frame, a mudguard cover, a hydraulic cylinder, and the like according to a second embodiment of the present invention.

12 is an enlarged cross-sectional view as seen from the direction of arrows XII-XII in FIG.

FIG. 13 is an enlarged sectional view of a main part showing a mudguard cover, a first hydraulic cylinder, a second hydraulic cylinder, and the like according to a third embodiment of the present invention.

FIG. 14 is an enlarged cross-sectional view of the first hydraulic cylinder and the guide as viewed from the direction indicated by arrows XIV-XIV in FIG.

FIG. 15 is a hydraulic circuit diagram for driving a first hydraulic cylinder and a second hydraulic cylinder according to a third embodiment.

FIG. 16 is a characteristic diagram showing a relationship between a stroke amount of a first hydraulic cylinder and time.

FIG. 17 is a characteristic diagram illustrating a relationship between a stroke amount of a second hydraulic cylinder and time.

FIG. 18 is a characteristic diagram showing a relationship between a stroke amount of a first hydraulic cylinder and a stroke amount of a second hydraulic cylinder.

FIG. 19 shows a track frame according to a fourth embodiment;
It is a top view which shows a mudguard cover, a hydraulic cylinder, etc.

20 is a perspective view showing a track frame, a mudguard cover, and the like in FIG. 19;

21 is an enlarged cross-sectional view as seen from the direction indicated by arrows XXI-XXI in FIG.

FIG. 22 is a hydraulic circuit diagram for driving a hydraulic cylinder according to a fourth embodiment.

FIG. 23 is a characteristic diagram showing a relationship between a control signal output from the signal generator in FIG. 22 and time.

FIG. 24 is a characteristic diagram showing a relationship between a stroke amount of a hydraulic cylinder and time in FIG. 22;

FIG. 25 is a hydraulic circuit diagram for driving a hydraulic cylinder according to a fifth embodiment.

FIG. 26 is a characteristic diagram showing a relationship between a control signal output from the signal generator in FIG. 25 and time.

FIG. 27 is a characteristic diagram showing a relationship between a stroke amount of a hydraulic cylinder and time in FIG. 25;

FIG. 28 is a hydraulic circuit diagram for driving a hydraulic cylinder according to a sixth embodiment.

FIG. 29 is a characteristic diagram showing a relationship between a control signal output from the signal generator in FIG. 28 and time.

FIG. 30 is a characteristic diagram showing a relationship between a stroke amount of a hydraulic cylinder and time in FIG. 28;

FIG. 31 is a perspective view showing a track frame, a mudguard cover, and the like according to a seventh embodiment.

FIG. 32 is a perspective view showing a track frame, a mudguard cover, and the like according to an eighth embodiment.

FIG. 33 is an enlarged sectional view as seen from the direction of arrows XXXIII-XXXIII in FIG. 32;

FIG. 34 is a hydraulic circuit diagram for driving a hydraulic cylinder according to a ninth embodiment.

FIG. 35 is a plan view showing a track frame, a mudguard cover, and the like according to a tenth embodiment.

FIG. 36 is an enlarged sectional view as seen from the direction of arrows XXXVI-XXXVI in FIG. 35;

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Lower traveling body 7 Track frame 8 Center frame 11 Side frame 11A Upper plate part 16 Idler wheel 17 Drive wheel 18 Crawler track 21, 51, 71, 81, 91, 101, 111, 12
1,142 Mudguard cover 22 Coating layer (film) 24, 73, 82, 92, 122, 141 Hydraulic cylinder (vibration actuator) 24A, 53A, 56A, 73A, 82A, 92A, 1
22A, 141A tube 24B, 53B, 73B, 82B, 92B, 122B
Piston 24C, 53C, 56B, 73C, 82C, 141B
Rods 24D, 24E, 53E, 53F, 73D, 73E, 8
2D, 82E, 92E, 92F, 122E, 122F
Oil chamber 25 Hydraulic pump (hydraulic source) 26 Tank 27A, 27B, 58A, 58B, 60A, 60B, 7
4A, 74B, 83A, 83B, 93A, 93B, 9
5, 123, 124, 125 Pipeline 53 First hydraulic cylinder (first vibration actuator) 56 Second hydraulic cylinder (second vibration actuator) 62, 76, 85, 96 Signal generator 75, 84 , 94 Solenoid valve (vibration control valve) 86 Slow return valve 102, 103, 112, 113, 114, 115 Cover body 104 Bolt (connecting tool) 116 Hinge (connecting tool) 92C, 122C Large diameter rod 126 Hydraulic pilot type Switching valve 129 Control valve

Claims (13)

[Claims] 1. A track frame having side frames provided on both left and right sides of a center frame, idler wheels provided on one side in front and rear of the side frames, and front and rear of each side frame. A driving wheel provided on the other side of the direction, a crawler belt wound between the idler wheel and the driving wheel,
A tracked vehicle comprising a mudguard cover provided on the track frame and located between an upper surface of the side frame and a crawler belt, and covering the track frame from above, wherein the mudguard cover is moved from the center frame to the side frame. And left and right diagonally downward,
A track-mounted vehicle characterized in that a vibration actuator that vibrates the mudguard cover in the left and right horizontal directions is provided between the track frame and the mudguard cover. 2. The vibrating actuator includes a hydraulic cylinder that repeatedly expands and contracts a rod from the tube in the left and right horizontal directions by repeatedly supplying and discharging pressure oil from the outside. The tracked vehicle according to claim 1, wherein the rod is mounted on a center frame side, and the rod is mounted on the mudguard cover side such that the mudguard cover vibrates in a horizontal direction. 3. A track frame provided with side frames on both left and right sides of a center frame, idler wheels provided on one side in front and rear of the side frames, and front and rear of each side frame. A driving wheel provided on the other side of the direction, a crawler belt wound between the idler wheel and the driving wheel,
A tracked vehicle comprising a mudguard cover provided on the track frame and located between an upper surface of the side frame and a crawler belt, and covering the track frame from above, wherein the mudguard cover is moved from the center frame to the side frame. And left and right diagonally downward,
Between the track frame and the mudguard cover, a first vibrating actuator that vibrates the mudguard cover in an inclined direction and a second vibrating actuator that vibrates the mudguard cover in a direction different from the first vibrating actuator. 2. A tracked vehicle, wherein the vibration actuator is provided. 4. The first and second vibrating actuators are configured to vibrate the mudguard cover with a phase difference with respect to each other, thereby adding a vibration giving circular motion or elliptical motion to the mudguard cover. Claim 3
A tracked vehicle according to claim 1. 5. The first vibrating actuator vibrates the mudguard cover in an inclined direction, the second vibrating actuator vibrates the mudguard cover in an inclined direction and a plate thickness direction, and 4. The track mounting according to claim 3, wherein the first and second vibration actuators are configured to vibrate with a phase difference of 90 degrees from each other to add vibration that gives a circular motion or an elliptical motion to the mudguard cover. 5. Type vehicle. 6. A track frame provided with side frames on both left and right sides of a center frame, idler wheels provided on one side in front and rear of the side frames, and front and rear of each side frame. A driving wheel provided on the other side of the direction, a crawler belt wound between the idler wheel and the driving wheel,
A tracked vehicle comprising a mudguard cover provided on the track frame and positioned between an upper surface of the side frame and a crawler belt and covering the track frame from above, provided between the track frame and the mudguard cover. A vibrating actuator for repeatedly vibrating the mudguard cover by supplying and discharging pressure oil from a hydraulic source, and a pressure provided between the vibrating actuator and the hydraulic source to supply and discharge the vibrating actuator. A tracked vehicle comprising: an actuator control means for controlling the oil to drive the vibrating actuator faster on one side of the vibration direction and slower on the other side. 7. The actuator control means according to claim 1, wherein the movement when the mudguard cover is displaced from the side frame toward the center frame by the vibrating actuator is more than the movement when the mud cover is displaced from the center frame to the side frame. 7. The tracked vehicle according to claim 6, wherein the supply and discharge of the pressure oil to and from the vibration actuator are controlled so as to increase the speed. 8. The mudguard cover is disposed obliquely downward and leftward and rightward from the center frame to the side frame side, and the vibrating actuator is an actuator that vibrates the mudguard cover in the inclined direction. The actuator control means makes the movement when the mudguard cover is displaced from the side frame to the center frame side by the vibration actuator faster than the movement when the mud cover is displaced from the center frame to the side frame side. 7. The tracked vehicle according to claim 6, wherein the supply and discharge of the pressure oil to and from the vibration actuator are controlled. 9. The actuator control means is provided in the middle of a pair of conduits connecting the vibration actuator to the hydraulic pressure source, and controls the pressure oil to the vibration actuator in response to an external control signal. 8. A vibration control valve for switching a supply / discharge direction, and signal output means for outputting the control signal to the vibration control valve as a signal having a sawtooth waveform. Or a tracked vehicle according to 8. 10. The vibration control, wherein the actuator control means is provided in the middle of a pair of pipes connecting the vibration actuator to the hydraulic pressure source and switches a supply / discharge direction of pressure oil to and from the vibration actuator. A valve and a slow return valve provided in the middle of the conduit to provide a throttling effect on pressure oil discharged from the vibration actuator when the vibration actuator is displaced to the other side in the vibration direction. The tracked vehicle according to claim 6, 7 or 8, which is configured. 11. The vibrating actuator includes a tube attached to the center frame, a rod attached to the mudguard cover with a proximal end inserted into the tube and a distal end projected out of the tube, A piston provided on the base end side of the rod and slidably inserted into the tube; and two oil chambers defined in the tube by the piston and providing different pressure receiving areas to the piston. The actuator control means is provided in the middle between a pair of pipelines connecting the hydraulic cylinder to a hydraulic pressure source,
A first switching position for supplying the pressure oil to the oil chamber having the smaller pressure receiving area of the two oil chambers and discharging the pressure oil from the larger oil chamber; and supplying the pressure oil to both the oil chambers. 9. The tracked vehicle according to claim 6, 7 or 8, comprising a vibration control valve selectively switched to a second switching position. 12. A water repellent film is formed on a surface side of the mudguard cover.
The tracked vehicle according to 7, 8, 9, 10, or 11. 13. The mudguard cover according to claim 1, wherein the cover is divided into a plurality of sheets in the front and rear directions or in the left and right directions, and these covers are integrally connected to each other by using a connection tool.
The tracked vehicle according to 3, 4, 5, 6, 7, 8, 9, 10, 11 or 12.